Cooling apparatus

ABSTRACT

There is provided a cooling apparatus which can improve a cooling efficiency while preventing an abnormal increase in pressure of a high side. The cooling apparatus comprises: a refrigerant circuit which uses carbon dioxide as a refrigerant; a control device which controls a speed of rotation of the compressor between predetermined lowest and highest speeds; and a cooled state sensor which detects a cooled state in a refrigerator main body to be cooled by an evaporator included in the refrigerant circuit. The control device increases a highest speed of rotation of the compressor if a temperature in the chamber of the refrigerator main body detected by the cooled state sensor is low.

This application is a divisional of application Ser. No. 10/847,848,filed May 19, 2004.

BACKGROUND OF THE INVENTION

The present invention relates to a cooling apparatus equipped with arefrigerant circuit which includes a compressor capable of controlling aspeed of rotation and uses carbon dioxide as a refrigerant.

In a conventional cooling apparatus of such a kind, e.g., a showcaseinstalled at a store, a refrigerant circuit is constituted bysequentially connecting a compressor, a gas cooler (condenser) anddiaphragmming means (capillary tube or the like) which constitute acondensing unit and an evaporator installed on a showcase main body sidethrough a pipe in an annular shape. A refrigerant gas compressed by thecompressor to become high in temperature and pressure is discharged tothe gas cooler. Heat is radiated from the refrigerant gas at the gascooler, and then the refrigerant gas is diaphragmmed by thediaphragmming means to be fed to the evaporator. The refrigerantevaporates there, and absorbs heat from its surroundings to exhibit acooling function, thereby cooling the chamber (space to be cooled) ofthe showcase (e.g., see Japanese Patent Application Laid-Open No.11-257830).

For the compressor, a speed of rotation is normally controlled between alowest speed and a highest speed by a control device. That is, when atemperature in the chamber of the showcase reaches an upper limit, thecontrol device starts (turns ON) the compressor. Then, the controldevice controls a speed of rotation of the compressor within a range ofpreset lowest and highest speeds based on outputs from various sensorsfor detecting a temperature of the refrigerant. When the temperature inthe chamber of the showcase drops to a lower limit, the compressor isstopped (turned OFF). Accordingly, a predetermined temperature ismaintained in the chamber of the showcase.

Incidentally, in order to solve a problem of ozone layer destruction, aproposal has recently been made to use carbon dioxide as a refrigerantin the cooling apparatus of the described kind. In the case of using thecarbon dioxide as the refrigerant in the cooling apparatus, however, acompression ratio becomes very high, and a temperature of the compressoritself and a temperature of a refrigerant gas discharged into therefrigerant circuit become high. Consequently, it is difficult to obtaina desired cooling efficiency.

Efforts have therefore been made to improve a cooling efficiency at theevaporator by raising a speed of rotation of the compressor to increasean amount of a refrigerant circulated in the refrigerant circuit,disposing an internal heat exchanger to exchange heat between arefrigerant of a high pressure side and a refrigerant of a low pressureside, supercooling the refrigerant of the high pressure side or thelike.

However, if the carbon dioxide is used as the refrigerant, the highpressure side of the refrigerant circuit may become supercritical.Consequently, pressure of the high side is not determinate due to anoutside air temperature, design pressure of a device is exceededespecially at the time of starting or a high outside air temperature,and there is a fear of damage to the device in the worst case. Thus, thecompressor has conventionally been controlled to a highest speed ofrotation in order to prevent such high pressure abnormalities,consequently creating a problem of a reduced cooling efficiency.

SUMMARY OF THE INVENTION

The present invention has been made to solve the foregoing technicalproblems, and designed to provide a cooling apparatus which can improvea cooling efficiency while preventing an abnormal increase in pressureof a high side.

A first aspect of the present invention is directed to a coolingapparatus comprising a refrigerant circuit which uses carbon dioxide asa refrigerant; a control device which controls a speed of rotation ofthe compressor between predetermined lowest and highest speeds; and acooled state sensor capable of detecting a cooled state of a space to becooled by an evaporator included in the refrigerant circuit, wherein thecontrol device increases a highest speed of rotation of the compressorif a temperature of the cooled space detected by the cooled state sensoris low.

A second aspect of the present invention is directed to the abovecooling apparatus, which further comprises an outside air temperaturesensor which detects an outside air temperature, wherein the controldevice increases the highest speed of rotation of the compressor whenthe outside air temperature detected by the outside air temperaturesensor is high, and reduces the highest speed of rotation of thecompressor when the outside air temperature is low.

Another object of the present invention is to improve a coolingefficiency at an evaporator while preventing an abnormal increase inpressure of a high side of a cooling apparatus.

A third aspect of the present invention is directed to a coolingapparatus comprising a control device which controls a speed of rotationof the compressor; and a cooled state sensor capable of detecting acooled state of a space to be cooled by an evaporator included in therefrigerant circuit, wherein the control device sets a targetevaporation temperature of the refrigerant at the evaporator based on atemperature of the cooled space detected by the cooled state sensor, andcontrols the speed of rotation of the compressor so as to set anevaporation temperature of the refrigerant equal to the targetevaporation temperature at the evaporator.

A fourth aspect of the present invention is directed to the abovecooling apparatus, wherein the control device sets the targetevaporation temperature of the refrigerant at the evaporator in arelation of being higher as the temperature of the cooled space ishigher based on the temperature of the cooled space detected by thecooled state sensor.

A fifth aspect of the present invention is directed to the above coolingapparatus, wherein the control device sets the target evaporationtemperature in a relation of being small in change thereof whichaccompanies a change in the temperature of the cooled space in a regionof a high temperature of the cooled space detected by the cooled statesensor, and large in change thereof which accompanies a change in thetemperature of the cooled space in a region of a low temperature of thecooled space.

A sixth aspect of the present invention is directed to the above coolingapparatus, which further comprises an outside air temperature sensorwhich detects an outside air temperature, wherein the control devicecorrects the target evaporation temperature to be high when the outsideair temperature detected by the outside air temperature sensor is high.

A seventh aspect of the present invention is directed to the abovecooling apparatus, wherein the control device corrects the targetevaporation temperature in the region of the high temperature of thecooled space detected by the cooled state sensor based on the outsideair temperature.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a refrigerant circuit diagram of a cooling apparatus accordingto the present invention;

FIG. 2 is a view showing changes in a speed of rotation of a compressor,pressure of a high side, a temperature in the chamber of a refrigeratormain body, and an evaporation temperature of a refrigerant in thecooling apparatus of the invention;

FIG. 3 is a flowchart showing rotational speed control of the compressorby a control device of the cooling apparatus of the invention;

FIG. 4 is a view showing changes in a speed of rotation of thecompressor and pressure of the high side at the time of starting;

FIG. 5 is a view showing a relation between an outside air temperatureand a highest speed of rotation of the compressor in the coolingapparatus of the invention;

FIG. 6 is a view showing a relation between a target evaporationtemperature and a temperature in the chamber at each outside airtemperature in the cooling apparatus of the invention; and

FIG. 7 is a view showing a change in temperature in the chamber of thecooling apparatus of the invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

Next, the preferred embodiment of the present invention will bedescribed in detail with reference to the accompanying drawings. Acooling apparatus 110 of FIG. 1 comprises a condensing unit 100 and arefrigerator main body 105 which becomes a cooler main body. The coolingapparatus 110 of the embodiment is, e.g., a showcase installed at astore. Thus, the refrigerator main body 105 is constituted of anadiabatic wall of a showcase.

The condensing unit 100 comprises a compressor 10, a gas cooler(condenser) 40, a capillary tube 58 etc., and is connected through apipe to an evaporator 92 of a refrigerator main body 105 (describedlater). The compressor 10, the gas cooler 40 and the capillary tube 58constitute a predetermined refrigerant circuit together with theevaporator 92.

That is, a refrigerant discharge tube 24 of the compressor 10 isconnected to an inlet of the gas cooler 40. Here, according to theembodiment, the compressor 10 is a multistage (two stages) compressiontype rotary compressor of an internal intermediate pressure type whichuses carbon dioxide (CO₂) as a refrigerant. The compressor 10 comprisesan electric element disposed as a driving element in a sealed container(not shown), and first and second rotary compression elements (1st and2nd stages) driven by the electric element.

In the drawing, a reference numeral 20 denotes a refrigerantintroduction tube compressed by the first rotary compression element ofthe compressor 10 to discharge the refrigerant to the outside from thesealed container first and then to introduce the refrigerant into thesecond rotary compression element. One end of the refrigerantintroduction tube 20 is communicated with a cylinder (not shown) of thesecond rotary compression element. The other end of the refrigerantintroduction tube 20 is communicated through an intermediate coolingcircuit 35 disposed in the gas cooler 40 (described later) with theinside of the sealed container.

In the drawing, a reference numeral 22 denotes a refrigerantintroduction tube for introducing the refrigerant into a cylinder (notshown) of the first rotary compression element of the compressor 10. Oneend of the refrigerant introduction tube 22 is communicated with thecylinder (not shown) of the first rotary compression element. The otherend of the refrigerant introduction tube 22 is connected to one end of astrainer 56. The strainer 56 captures and filters foreign objects suchas dusts or chips mixed in a refrigerant gas circulated in therefrigerant circuit, and comprises an opening formed on the other endside thereof and a filter (not shown) of a roughly conical shape taperedfrom the opening toward one end side thereof. The opening of the fileris mounted in a state of being bonded to a refrigerant pipe 28 connectedto the other end of the strainer 56.

Additionally, the refrigerant discharge tube 24 is a refrigerant pipefor discharging the refrigerant compressed by the second rotarycompression element to the gas cooler 40.

The gas cooler 40 comprises a refrigerant pipe and a heat exchanging findisposed heat-exchangeably in the refrigerant pipe. The refrigerant pipe24 is communicated and connected to an inlet side of the refrigerantpipe of the gas cooler 40. An outside air temperature sensor 74 isdisposed as a temperature sensor in the gas cooler 40 to detect anoutside air temperature. The outside air temperature sensor 74 isconnected to a microcomputer 80 (described later) as a control device ofthe condensing unit 100.

A refrigerant pipe 26 connected to an outlet side of the refrigerantpipe which constitutes the gas cooler 40 passes through an internal heatexchanger 50. The internal heat exchanger 50 heat-exchanges arefrigerant of a high pressure side from the second rotary compressionelement which is discharged from the gas cooler 40 with a refrigerant ofa low pressure side which is discharged from the evaporator 92 disposedin the refrigerator main body 105. The refrigerant pipe 26 of the highpressure side passed through the internal heat exchanger 50 is passedthrough a strainer 54 similar to the above to reach the capillary tube58 as diaphramming means.

One end of a refrigerant pipe 94 of the refrigerator main body 105 isdetachably connected to the refrigerant pipe 26 of the condensing unit100 by a swage locking joint as connection means.

Meanwhile, the refrigerant pipe 28 connected to the other end of thestrainer 56 is detachably connected to the refrigerant pipe 94 by aswage locking joint as connection means similar to the above which ispassed through the internal heat exchanger 50 to be attached to theother end of the refrigerant pipe 94 of the refrigerator main body 105.

The refrigerant discharge tube 24 includes a discharge temperaturesensor 70 disposed to detect a temperature of a refrigerant gasdischarged from the compressor 10, and a high pressure switch 72disposed to detect pressure of the refrigerant gas. These components areconnected to the microcomputer 80.

The refrigerant pipe 26 out of the capillary tube 58 includes arefrigerant temperature sensor 76 disposed to detect a temperature of arefrigerant out of the capillary tube 58. This component is alsoconnected to the microcomputer 80. Further, on the inlet side of theinternal heat exchanger 50 of the refrigerant pipe 28, a returntemperature sensor 78 is disposed to detect a temperature of therefrigerant out of the evaporator 92 of the refrigerator main body 105.This return temperature sensor 78 is also connected to the microcomputer80.

A reference numeral 40F denotes a fan for venting the gas cooler 40 toair-cool it. A reference numeral 92F denotes a fan for circulating achill heat-exchanged with the evaporator 92 disposed in a duct (notshown) of the refrigerator main body 105 therein which is a space to becooled by the evaporator 92. A reference numeral 65 denotes a currentsensor for detecting an energizing current of the electric element ofthe compressor 10 to control running. The fan 40F and the current sensor65 are connected to the microcomputer 80 of the condensing unit 100,while the fan 92F is connected to a control device 90 (described later)of the refrigerator main body 105.

Here, the microcomputer 80 is a control device for controlling thecondensing unit 100. Signal lines from the discharge temperature sensor70, the high pressure switch 72, the outside air temperature sensor 74,the refrigerant temperature sensor 76, the return temperature sensor 78,the current sensor 65, a temperature sensor in the chamber 91 (describedlater) disposed in the refrigerator main body 105, and the controldevice 90 as control means of the refrigerator main body 105 areconnected to an input of the microcomputer 80. Based on these inputs,the microcomputer 80 controls a speed of rotation of the compressor 10connected to an output by an inverter substrate (not shown, connected tothe output to the microcomputer 80), and controls running of the fan40F.

The control device 90 of the refrigerator main body 105 includes thetemperature sensor in the chamber 91 disposed to detect the temperaturein the chamber, a temperature control dial disposed to control thetemperature in the chamber, a function disposed to stop the compressor10 etc. Based on these outputs, the control device 90 controls the fan92F, and sends an ON/OFF signal through the signal line to themicrocomputer 80 of the condensing unit 100.

As the refrigerant of the cooling apparatus 110, the aforementionedcarbon dioxide (CO₂) which is a natural refrigerant is used inconsideration of friendliness to a global environment, combustibility,toxicity etc. As oil which is lubricating oil, for example, existing oilsuch as mineral oil, alkylbenzene oil, ether oil, ester oil orpolyalkylene glycol (PGA) is used.

The refrigerator main body 105 is constituted of an adiabatic wall as awhole, and a chamber as a space to be cooled is constituted in theadiabatic wall. The duct is partitioned from the chamber in theadiabatic wall. The evaporator 92 and the fan 92F are arranged in theduct. The evaporator 92 comprises the refrigerant pipe 94 of ameandering shape, and a fan (not shown) for heat-exchanging. Both endsof the refrigerant pipe 94 are detachably connected to the refrigerantpipes 26, 28 of the condensing unit 100 by the swage locking joint (notshown) as described above.

Next, description will be made of an operation of the cooling apparatus110 of the invention constituted in the foregoing manner with referenceto FIGS. 2 to 7. FIG. 2 is a view showing changes in a speed of rotationof the compressor 10, pressure of a high side, temperature in thechamber of the refrigerator main body 105, and evaporation temperatureof the refrigerant in the evaporator 92. FIG. 3 is a flowchart showing acontrol operation of the microcomputer 80.

(1) Start of Compressor Control

When a start switch (not shown) disposed in the refrigerator main body105 is turned ON or a power socket of the refrigerator main body 105 isconnected to a power outlet, power is supplied to the microcomputer 80(step S1 of FIG. 3) to enter initial setting in step S2.

In the initial setting, the inverter substrate is initialized to start aprogram. Upon the start of the program, the microcomputer 80 readsvarious functions or a constant from a ROM in step S3. In the readingfrom the ROM of step S3, rotational speed information other than ahighest speed of rotation of the compressor 10, and a parameter(described later) necessary for calculating a highest speed of rotation(step S13 of FIG. 3) are read.

After completion of the reading from the ROM in step S3 of FIG. 3, themicrocomputer 80 proceeds to step S4 to read sensor information of thedischarge temperature sensor 70, the outside air temperature sensor 74,the refrigerant temperature sensor 76, the return temperature sensor 78or the like, and a control signal of the pressure switch 72, theinverter or the like. Next, the microcomputer 80 enters abnormalitydetermination of step S5.

In step S5, the microcomputer 80 determines turning ON/OFF of thepressure switch 72, a temperature detected by each sensor, a currentabnormality or the like. Here, if an abnormality is discovered in eachsensor or a current value, or if the pressure switch 72 is OFF, themicrocomputer 80 proceeds to step S6 to light a predetermined LED (lampfor notifying an occurrence of an abnormality), and stops running of thecompressor 10 at the time of its running. Incidentally, the pressureswitch 72 senses an abnormal increase of the pressure of the high side.The switch is turned OFF when pressure of the refrigerant passed throughthe refrigerant discharge tube 24 becomes, e.g., 13.5 MPaG or higher,and turned ON again when the pressure becomes 9.5 MPaG or lower.

Thus, upon notification of the abnormality occurrence in step S6, themicrocomputer 80 stands by for a predetermined time, and then returns tostep S1 to repeat the aforementioned operation.

On the other hand, if no abnormality is recognized in the temperaturedetected by each sensor, the current value or the like, and if thepressure switch 72 is ON in step S5, the microcomputer 80 proceeds tostep S7 to enter defrosting determination (described later). Here, if aneed to defrost the evaporator 92 is determined, the microcomputer 80proceeds to step S8 to stop the running of the compressor 10, andrepeats the operation from step S4 to step S9 until completion of thedefrosting is determined in step S9.

On the other hand, if no need to defrost the evaporator 92 is determinedin step S7, or if defrosting completion is determined in step S9, themicrocomputer 80 proceeds to step S10 to calculate rotational speedholding time of the compressor 10.

(2) Rotational Speed Holding Control of Compressor Start

Here, the rotational speed holding of the compressor 10 means runningthereof while the microcomputer 80 holds a speed of rotation lower thana lowest speed of rotation for a predetermined time at the time ofstarting. That is, the microcomputer 80 sets a target speed of rotationwithin a range of a highest speed of rotation (Ma×Hz) obtained incalculation of a highest rotational speed of step S13 (described later)during normal running and a lowest speed of rotation read beforehand instep S3 to run the compressor 10. At the time of starting, however, themicrocomputer 80 holds a speed of rotation lower than the lowestrotational speed for a predetermined time before the lowest rotationalspeed is reached to run the compressor 10 (state of (1) of FIG. 2).

For example, if the lowest rotational speed read from the ROM in step S3of FIG. 3, the microcomputer 80 holds a speed of rotation (25 Hzaccording to the embodiment) equal to/lower than 90% of 30 Hz for apredetermined time to run the compressor 10.

The above state will be described in detail with reference to FIG. 4. Ifthe microcomputer 80 starts running of the compressor 10 at 30 Hz whichis a lowest speed of rotation without holding a speed of rotation lowerthan the lowest rotational speed for a predetermined time different fromthe conventional case, pressure of a high side suddenly increases at thetime of starting as indicated by a broken line of FIG. 4, and there is afear that design pressure (limit of withstand pressure) of the device,the pipe or the like disposed in the refrigerant circuit may be exceededin a worst case. Assuming that a lowest speed of rotation is preset to30 Hz or lower to run the compressor 10, if the rotational speed islowered below 30 Hz during running, there occurs a problem of aconsiderable increase in noise or vibration generated from thecompressor 10.

However, if the microcomputer 80 runs the compressor 10 by holding thespeed of rotation (25 Hz) lower than the lowest rotational speed for apredetermined time before the rotational speed of the compressor 10reaches a predetermined rotational speed at the time of starting asindicated by a solid line of FIG. 4, it is possible to prevent anabnormal increase in the pressure of the high side.

Additionally, since the rotational speed never drops below 30 Hz duringrunning, it is possible to suppress even noise or vibration from thecompressor 10.

Further, the holding time of the rotational speed is decided based onthe temperature in the chamber of the refrigerator main body 105 whichis a temperature of the space to be cooled by evaporator 92 in step S10.That is, according to the embodiment, if a temperature in the chamberdetected by the temperature sensor in the chamber 91 as a cooled statesensor is equal to/lower than +20° C., the microcomputer 80 runs thecompressor 10 by holding its rotational speed at 25 Hz for, e.g., 30sec., and then increases the rotational speed to the lowest rotationalspeed (30 Hz) (state of (2) in FIG. 3). In other words, if thetemperature in the chamber of the refrigerator main body 105 is equalto/lower than +20° C., a temperature is low in the evaporator, and thereare many refrigerants. Thus, even without setting a holding time solong, an abnormal increase in the pressure of the high side can beprevented to shorten the holding time. Accordingly, since it is possibleto transfer to normal rotational speed control based on highest andlowest rotational speeds within a short time, the chamber of therefrigerator main body 105 can be quickly cooled.

Therefore, it is possible to prevent an abnormal increase in thepressure of the high side while suppressing a reduction in a coolingefficiency in the refrigerator main body 105 as much as possible.

On the other hand, if the temperature in the chamber detected by thetemperature sensor in the chamber 91 is higher than +20° C., themicrocomputer 80 runs the compressor 10 by holding its speed of rotationat 25 Hz for 10 sec., and then increases the speed of rotation to thelowest rotational speed. If the temperature in the chamber of therefrigerator main body 105 is higher than +20° C., a state is unstablein the refrigerant cycle and the pressure of the high side is easilyincreased. In other words, if the holding time is 30 sec. as describedabove, the holding time of the rotational speed is too short to preventan abnormal increase in the pressure of the high side. Thus, byextending the holding time to 10 min., it is possible to surely preventthe abnormal increase of the high pressure side, and to secure a stablerunning state.

Therefore, after the start of the compressor, the microcomputer 80 runsit by holding the rotational speed at 25 Hz for the predetermined timebefore the lowest rotational speed is reached, and properly changes theholding time based on the temperature in the chamber of the refrigeratormain body 105, whereby the abnormal increase in the pressure of the highside can be effectively prevented, and reliability and performance ofthe cooling apparatus 110 can be improved.

After the rotational speed holding time of the compressor 10 iscalculated based on the temperature in the chamber in step S10 of FIG. 3as described above, the microcomputer 80 starts the compressor 10 instep S11. Then, the running time thus far is compared with the holdingtime calculated in step S10. If the running time from the start of thecompressor 10 is shorter than the holding time calculated in step S10,the process proceeds to step S12. Here, the microcomputer 80 sets theaforementioned starting time Hz of 25 Hz equal to a target rotationalspeed of the compressor 10, and proceeds to step S20. Subsequently, instep S20, the compressor 10 is run at a rotational speed of 25 Hz by theinverter substrate as described later.

That is, upon a start of the electric element of the compressor 10 atthe aforementioned rotational speed, a refrigerant is sucked into thefirst rotary compression element of the compressor 10 to be compressed,and then discharged into the sealed container. The refrigerant gasdischarged into the sealed container enters the refrigerant introductiontube 20, and goes out of the compressor 10 to flow into the intermediatecooling circuit 35. The intermediate cooling circuit 35 radiates heat byan air cooling system while passing through the gas cooler 40.

Accordingly, since the refrigerant sucked into the second rotarycompression element can be cooled, a temperature increase can besuppressed in the sealed container, and compression efficiency of thesecond rotary compression element can be improved. Moreover, it ispossible to suppress a temperature increase of the refrigerantcompressed by the second rotary compression element to be discharged.

Then, the cooled refrigerant gas of intermediate pressure is sucked intothe second rotary compression element of the compressor 10, subjected tocompression of the second stage to become a refrigerant gas of highpressure and a high temperature, and discharged through the refrigerantdischarge tube 24 to the outside. By this time, the refrigerant has beencompressed to proper supercritical pressure. The refrigerant gasdischarged from the refrigerant discharge tube 24 flows into the gascooler 40, radiates heat therein by the air cooling system, and thenpasses through the internal heat exchanger 50. Heat of the refrigerantis removed by the refrigerant of the low pressure side there to befurther cooled.

Because of the presence of the internal heat exchanger 50, the heat ofthe refrigerant discharged out of the gas cooler 40 to pass through theinternal heat exchanger 50 is removed by the refrigerant of the lowpressure side, and thus a supercooling degree of the refrigerant becomeslarger by a corresponding amount. As a result, the cooling efficiency ofthe evaporator 92 can be improved.

The refrigerant gas of the high pressure side cooled by the internalheat exchanger 50 is passed through the strainer 54 to reach thecapillary tube 58. The pressure of the refrigerant is lowered in thecapillary tube 58, and then passed through the swage locking joint (notshown) to flow from the refrigerant pipe 94 of the refrigerator mainbody 105 into the evaporator 92. The refrigerant evaporates there, andsucks heat from surrounding air to exhibit a cooling function, therebycooling the chamber of the refrigerator main body 105.

Subsequently, the refrigerant flows out of the evaporator 92, passesfrom the refrigerant pipe 94 through the swage locking joint (not shown)to enter the refrigerant pipe 26 of the condensing unit 100, and reachesthe internal heat exchanger 50. Heat is removed from the refrigerant ofthe high pressure side there, and the refrigerant is subjected to aheating operation. Here, the refrigerant evaporated by the evaporator 92to become low in temperature, and discharged therefrom is not completelyin a gas state but in a state of being mixed with a liquid. However, therefrigerant is passed through the internal heat exchanger 50 to beheat-exchanged with the refrigerant of the high pressure side, and thusthe refrigerant is heated. At a point of this time, the refrigerant issecured for a degree of superheat to become a gas completely.

Accordingly, since the refrigerant out of the evaporator 92 can besurely gasified, without disposing an accumulator or the like on the lowpressure side, it is possible to surely prevent liquid backing in whicha liquid refrigerant is sucked into the compressor 10, and a problem ofdamage given to the compressor 10 by liquid compression. Therefore, itis possible to improve reliability of the cooling apparatus 110.

Incidentally, the refrigerant heated by the internal heat exchanger 50repeats a cycle of being passed through the strainer 56 to be suckedfrom the refrigerant introduction tube 22 into the first rotarycompression element of the compressor 10.

(3) Control of Change in Highest Speed of Rotation of Compressor Basedon Outside Air Temperature

When time passes from the start, and the running time thus far reachesthe holding time calculated in step S10 of FIG. 3 in step S11, themicrocomputer 80 increases the rotational speed of the compressor 10 tothe lowest rotational speed (30 Hz) (state of (2) in FIG. 3). Then, themicrocomputer 80 proceeds from step S10 to step S13 to calculate ahighest speed of rotation (Ma×Hz). This highest rotational speed iscalculated based on an outside air temperature detected by the outsideair temperature sensor 74.

That is, the microcomputer 80 lowers the highest rotational speed of thecompressor 10 if the outside air temperature detected by the outside airtemperature sensor 74 is high, and increases the highest rotationalspeed thereof if the outside air temperature is low. The highestrotational speed is calculated within a range of preset upper and lowerlimit values (respectively 45 Hz and 30 Hz according to the embodiment)as shown in FIG. 5. This highest rotational speed is lowered in a linearfunctional manner when the outside air temperature increases, andincreased in the same manner when the outside air temperature decreasesas shown in FIG. 5.

If the outside air temperature is high, a temperature of the refrigerantcirculated in the refrigerant circuit becomes high to cause an easyabnormal increase in the pressure of the high side. Thus, by setting thehighest speed of rotation low, it is possible to prevent the abnormalincrease in the pressure of the high side as much as possible. On theother hand, if the outside air temperature is low, the temperature ofthe refrigerant circulated in the refrigerant circuit is low to make anabnormal increase difficult in the pressure of the high side. Thus, itis possible to set the highest speed of rotation high.

Therefore, since a target speed of rotation (described later) becomesequal to/lower than the highest rotational speed, by setting the highestrotational speed to a value in which an abnormal increase is difficultin the pressure of the high side, it is possible to effectively preventthe abnormal increase in the pressure of the high side.

(4) Target Evaporation Temperature Control at Evaporator

After the highest speed of rotation is decided in step S13 of FIG. 3 asdescribed above, the microcomputer 80 proceeds to step S14 to calculatea target evaporation temperature Teva. The microcomputer 80 presets atarget evaporation temperature of the refrigerant at the evaporator 92based on the temperature in the chamber of the refrigerator main body105 detected by the temperature sensor in the chamber 91, and sets thetarget rotational speed within the range of the highest and lowestrotational speeds of the compressor 10 so that an evaporationtemperature of the refrigerant which has flown into the evaporator 92can be the target evaporation temperature, thereby running thecompressor 10.

Then, the microcomputer 80 sets a target evaporation temperature of therefrigerant at the evaporator 92 in a relation of being higher as thetemperature in the chamber is higher based on the temperature in thechamber detected by the temperature sensor in the chamber 91.Calculation of the target evaporation temperature Teva in this case iscarried out in step S15.

That is, of Tya and Tyc calculated by two equations of Tya=Tx×0.35-8.5and Tyc=Tx×0.2-6+z, a smaller numerical value is set as a targetevaporation temperature Teva. Incidentally, in the equations, Tx denotesa temperature in the chamber (one of indexes indicating the cooled stateof the chamber which is a space to be cooled) detected by thetemperature sensor in the chamber 91, and z denotes a value (z=Tr(outside air temperature) −32) obtained by subtracting 32 (deg) from anoutside air temperature Tr detected by the outside air temperaturesensor 74.

FIG. 6 shows changes in the target evaporation temperature Teva at +32°C., +35° C. and +41° C. of the outside air temperatures Tr detected bythe outside air temperature sensor 74 in this case. As shown in FIG. 6,a change in the target evaporation temperature Teva set by the aboveequations after a change in the temperature in the chamber is small in aregion of a high temperature in the chamber Tx, and a change in thetarget evaporation temperature Teva after a changed in the temperaturein the chamber Tx is large in a region of a low temperature in thechamber Tx.

That is, the microcomputer 80 corrects the target evaporationtemperature Teva high if the outside air temperature Tr detected by theoutside air temperature sensor 74 is high, and corrects the targetevaporation temperature Teva based on the outside air temperature in aregion of a high temperature of the cooled space detected by thetemperature sensor in the chamber 91. Now, the target evaporationtemperature Teva when the outside air temperature is +32° C. isdescribed. When the temperature in the chamber is +7° C. or higher, adrop in the temperature in the chamber is accompanied by a relativelyslow reduction in the target evaporation temperature Teva. When thetemperature in the chamber is lower than +7° C., a drop in thetemperature in the chamber is accompanied by a sudden reduction in thetarget evaporation temperature Teva. That is, the refrigerant whichflows in the refrigerant circuit is unstable in the high temperature inthe chamber state. Thus, it is possible to prevent an abnormal increasein the pressure of the high side by setting the target evaporationtemperature Teva relatively high.

In the low temperature in the chamber state, the state of therefrigerant which flows in the refrigerant circuit becomes stable. Thus,by setting the target evaporation temperature Teva relatively low, thechamber of the refrigerator main body 105 can be quickly cooled. As aresult, it is possible to quickly lower the temperature in the chamberof the refrigerator main body 105 in restarting or the like afterdefrosting, and to maintain a temperature of articles housed therein ata proper value.

After the target evaporation temperature Teva is calculated by theaforementioned equation, the microcomputer 80 proceeds to step S14 tocompare a current evaporation temperature with the target evaporationtemperature Teva. If the current evaporation temperature is lower thanthe target evaporation temperature Teva, the rotational speed of thecompressor 10 is decreased in step S16. If the current evaporationtemperature is higher than the target evaporation temperature Teva, therotational speed of the compressor 10 is increased in step S17. Next, instep S18, the microcomputer 80 determines the range of the highest andlowest rotational speeds decided in step S13 and the rotational speedincreased/decreased in step S16 or S17.

Here, if the rotational speed increased/decreased in step S16 or S17 iswithin the range of the highest and lowest rotational speeds, therotational speed is set as a target rotational speed. The compressor 10is run by the inverter substrate at the target rotational speed in stepS20 as described above.

On the other hand, if the rotational speed increased/decreased in stepS16 or S17 is outside the range of the highest and lowest rotationalspeeds, the microcomputer 80 proceeds to step S19, makes adjustmentbased on the rotational speed increased/decreased in step S16 or S17 toachieve an optimal rotational speed within the range of the highest andlowest rotational speeds, sets the adjusted rotational speed as a targetrotational speed, and runs the electric element of the compressor 10 atthe target rotational speed in step S20. Thereafter, the process returnsto step S4 to repeat subsequent steps.

Incidentally, when the start switch (not shown) disposed in therefrigerator main body 105 is cut off, or the power socket thereof ispulled out of the power plug, the energization of the microcomputer 80is stopped (step S21 of FIG. 3), and thus the program is finished (stepS22).

(5) Defrosting Control of Evaporator

Meanwhile, when the chamber of the refrigerator main body 105 issufficiently cooled to lower the temperature in the chamber to a setlower limit (+3° C.), the control device 90 of the refrigerator mainbody 105 sends an OFF signal of the compressor 10 to the microcomputer80. Upon reception of the OFF signal, the microcomputer 80 determines astart of defrosting in defrosting determination of step S7 of FIG. 3,proceeds to step S8 to stop the running of the compressor 10, and startsdefrosting (OFF cycle defrosting) of the evaporator 92.

After the stop of the compressor 10, when the temperature in the chamberof the refrigerator main body 105 reaches a set upper limit (+7° C.),the control device 90 of the refrigerator main body 105 sends an ONsignal to the compressor 10 of the microcomputer 80. Upon reception ofthe ON signal, the microcomputer 80 determines completion of defrostingin step S9, and proceeds to step S10 and after to resume running of thecompressor 10 as described above.

(6) Forcible Stop of Compressor

Here, if the compressor 10 has been continuously run for a predeterminedtime, the microcomputer 80 determines a start of defrosting indefrosting determination of step S7 of FIG. 3, proceeds to step S8 toforcibly stop the running of the compressor 10, and then startsdefrosting of the evaporator 92. Additionally, the continuous runningtime of the compressor 10 for stopping the same is changed based on thetemperature in the chamber of the microcomputer 105 detected by thetemperature sensor in the chamber 91. In this case, the microcomputer 80sets the continuous running time of the compressor 10 for stopping thesame shorter as the temperature in the chamber is lower.

A specific reason is that if the temperature in the chamber of therefrigerator main body 105 is low, e.g., +10° C., there is a fear offreezing of articles or the like housed in the refrigerator main body105. Thus, according to the embodiment, for example, if the compressor10 is continuously run for 30 min., while the temperature in the chamberis +10° C. or lower, it is possible to prevent a problem of freezing ofthe articles housed in the chamber by forcibly stopping the runningthereof.

When the temperature in the chamber of the refrigerator main body 105reaches the set upper limit (+7° C.), the control device 90 of therefrigerator main body 105 sends an ON signal of the compressor 10 tothe microcomputer 80. Thus, the microcomputer 80 resumes running of thecompressor 10 as in the previous case (step S9 of FIG. 3).

On the other hand, if the compressor 10 has been run at a temperature inthe chamber higher than, e.g., +10° C., for a predetermined time, themicrocomputer 80 stops the running thereof. This is because if thecompressor 10 is continuously run for a long time, frosting occurs inthe evaporator 92, and the refrigerant which passes through theevaporator 92 cannot be heat-exchanged with surrounding air, creating afear of insufficient cooling of the chamber of the refrigerator mainbody 105. Thus, for example, if the compressor 10 is continuously run ata temperature in the chamber of a range higher than +10° C. to 20° C. orlower for 10 hours or more, or at a temperature in the chamber higherthan 20° C. for 20 hours or more, the microcomputer 80 determines astart of defrosting in defrosting determination of step S7, and forciblystops the running of the compressor 10 to execute defrosting of theevaporator 92 in step S8.

This state will be described with reference to FIG. 7. In FIG. 7, abroken line indicates a change in a temperature in the chamber when therunning of the compressor 10 is not stopped to execute defrosting in thecase of continuous running thereof at a temperature in the chamberhigher than +10° C. but equal to/lower than 20° C. detected by thetemperature sensor in the chamber 91 for 10 hours or more. A solid lineindicates a change in a temperature in the chamber when the running ofthe compressor 10 is stopped to execute defrosting in the case ofcontinuous running thereof at a temperature in the chamber higher than+10° C. but equal to/lower than +20° C. for 10 hours or more.

As shown in FIG. 7, the evaporator 92 can be defrosted by forciblystopping the compressor 10 in the case of continuous running thereof atthe temperature in the chamber higher than +10° C. but equal to/lowerthan +20° C. for 10 hours or more. Compared with the case of notstopping the compressor 10 to execute defrosting, a heat exchangingefficiency of the refrigerant in the evaporator 92 after the defrostingcan be improved, and the target temperature in the chamber can bereached early. Thus, it is possible to improve a cooling efficiency.

Furthermore, as the temperature in the chamber of the refrigerator mainbody 105 is lower, the continuous running time of the compressor 10 forstopping the same is set shorter. Thus, it is possible to preventfreezing of the articles housed therein when the temperature in thechamber is low while improving the heat exchanging efficiency of therefrigerant in the evaporator 92 after defrosting as described above.

(7) Control of Increase in Highest Rotational Speed of Compressor

Next, if the temperature in the chamber of the refrigerator main body105 detected by the temperature sensor in the chamber 91 is low, themicrocomputer 80 increases the highest rotational speed (Ma×Hz) of thecompressor 10. For example, when the temperature in the chamber of therefrigerator main body 105 is lowered to +20° C., the microcomputer 80slightly increases the highest rotational speed (e.g., 4 Hz) to run thecompressor 10 (state of (3) of FIG. 2). That is, in addition to theaforementioned control of the highest rotational speed based on theoutside air temperature, when the temperature in the chamber of therefrigerator main body 105 is lowered to +20° C., the microcomputer 80increases the highest rotational speed decided based on the outside airtemperature detected by the outside air temperature sensor 74 asdescribed above to 4 Hz to run the compressor 10.

When the temperature in the chamber of the refrigerator main body 105drops to +20° C. or lower, pressure of the low side becomes low.Accordingly, pressure of the high side is also lowered to stabilize therefrigerant in the refrigerant circuit. If the rotational speed isincreased in this state, even when the pressure of the high sideslightly increases as shown in (4) of FIG. 2, it is possible to preventa problem of an abnormal increase which exceeds design pressure of thedevice, the pipe or the like of the high side.

Additionally, an amount of a refrigerant circulated in the refrigerantcircuit is increased by increasing the highest rotational speed. Thus,an amount of a refrigerant heat-exchanged with air circulated in theevaporator 92 is increased to enable improvement of the coolingefficiency thereof. As a result, an evaporation temperature of therefrigerant in the evaporator 92 is also lowered as shown in (5) of FIG.2, and the chamber of the refrigerator main body 105 can be cooledearly.

As described above, the microcomputer 80 changes the highest rotationalspeed of the compressor 10 based on the outside air temperature detectedby the outside air temperature sensor 74, and increases the highestrotational speed to run the compressor 10 when the temperature in thechamber of the refrigerator main body 105 detected by the temperaturesensor in the chamber 91 is lowered to a predetermined temperature.Thus, it is possible to improve the cooling efficiency of the evaporator92 while preventing an abnormal increase in the pressure of the highside.

Further, since the chamber of the refrigerator main body 105 can becooled early, it is possible to improve performance of the coolingapparatus 110.

According to the embodiment, when the temperature in the chamber of therefrigerator main body 105 is lowered to +20° C., the microcomputer 80increases the highest rotational speed to 4 Hz to run the compressor 10.However, the temperature at which the microcomputer 80 increases thehighest rotational speed, and the numerical value of the increasedrotational speed are not limited to the foregoing. They can be properlychanged depending on a size of the cooling apparatus 110 and a purposeof use.

According to the embodiment, the microcomputer 80 changes the highestrotational speed of the compressor 10 based on the output of thetemperature sensor in the chamber 91 for directly detecting thetemperature in the chamber of the refrigerator main body 105. Notlimited to this, however, the microcomputer 80 may change the highestrotational speed of the compressor 10 based on, e.g., an output of thetemperature sensor for detecting the refrigerant temperature on theoutlet side of the evaporator 92. In such a case, by using thetemperature sensor used for superheat degree control or the like at theoutlet of the evaporator, the temperature sensor in the chamber can beremoved to reduce production costs.

Additionally, the microcomputer 80 may change the highest rotationalspeed of the compressor 10 based on an output of the temperature sensorfor detecting a temperature of articles housed in the refrigerator mainbody 105. In such a case, stricter control can be carried out based onthe temperature of the articles housed in the refrigerator main body105, whereby it is possible to improve control accuracy.

According to the embodiment, the microcomputer 80 forcibly stops therunning of the compressor 10 in the case of the continuous runningthereof at the temperature in the chamber of the refrigerator main body105 set to +10° C. or lower for 30 minutes or more, within thetemperature in the chamber range higher than +10° C. to +20° C. or lowerfor 10 hours or more, or at the temperature in the chamber higher than+20° C. for 20 hours or more. However, the continuous running time orthe temperature is not limited to such. Proper changes can be madedepending on a purpose of use etc.

According to the embodiment, the continuous running time is changedbased on the detection of the temperature sensor in the chamber 91 fordirectly detecting the temperature in the chamber of the refrigeratormain body 105. Not limited to this, however, the microcomputer 80 maychange the continuous running time based on, e.g., the output of thetemperature sensor for detecting the refrigerant temperature on theoutlet side of the evaporator 92. In such a case, by using thetemperature sensor used for superheat degree control or the like at theoutlet of the evaporator, the temperature sensor in the chamber can beremoved to reduce production costs.

Additionally, the continuous running time may be changed based on theoutput of the temperature sensor for detecting the temperature of thearticles housed in the refrigerator main body 105. In such a case,stricter control can be carried out based on the temperature of thearticles housed in the refrigerator main body 105, whereby it ispossible to improve control accuracy.

Furthermore, according to the embodiment, the cooling apparatus 110 isthe showcase installed at the store. Not limited to this, however, thecooling apparatus of the invention may be used as a refrigerator, anautomatic vending machine, or an air conditioner.

As described above in detail, according to the present invention, thecooling apparatus comprises the control device which controls the speedof rotation of the compressor between the predetermined lowest andhighest speeds, and the cooled state sensor which can detect the cooledstate of the space to be cooled by the evaporator included in therefrigerant circuit. The control device increases the highest speed ofrotation of the compressor if the temperature of the cooled spacedetected by the cooled state sensor is low. Thus, it is possible toimprove the cooling efficiency of the evaporator while preventing theabnormal increase in the pressure of the high side.

Therefore, since the space to be cooled by the evaporator is cooledearly, it is possible to improve the performance of the coolingapparatus.

According to the invention, in addition to the above, the coolingapparatus further comprises the outside air temperature sensor whichdetects the outside air temperature. The control device reduces thehighest speed of rotation of the compressor when the outside airtemperature detected by the outside air temperature sensor is high, andincreases the highest speed of rotation of the compressor when theoutside air temperature is low. Thus, it is possible to effectivelyprevent the abnormal increase in the pressure of the high side.

According to the present invention, the cooling apparatus comprises thecontrol device which controls the speed of rotation of the compressor,and the cooled state sensor which can detect the cooled state of thespace to be cooled by the evaporator included in the refrigerantcircuit. The control device sets the target evaporation temperature ofthe refrigerant at the evaporator based on the temperature of the cooledspace detected by the cooled state sensor, and controls the speed ofrotation of the compressor so as to set the evaporation temperature ofthe refrigerant equal to the target evaporation temperature at theevaporator. Thus, for example, based on the temperature of the cooledspace detected by the cooled state sensor, the control device sets thetarget evaporation temperature of the refrigerant in the evaporator inthe relation of being higher as the temperature of the cooled space ishigher, whereby it is possible to prevent the abnormal increase in thepressure of the high side.

Therefore, the rotational speed of the compressor can be set to anoptical speed to improve the reliability and performance of the coolingapparatus.

According to the invention, the control device sets the targetevaporation temperature in the relation of being small in change thereofwhich accompanies a change in the temperature of the cooled space in theregion of the high temperature of the cooled space detected by thecooled state sensor, and large in change thereof which accompanies achange in the temperature of the cooled space in the region of the lowtemperature of the cooled space. Thus, it is possible to improve thecooling efficiency in the low temperature region of the cooled spacewhile effectively preventing the abnormal increase in the pressure ofthe high side which easily occurs in the high temperature regionthereof.

Furthermore, in addition to the above, according to the invention, thecooling apparatus further comprises the outside air temperature sensorwhich detects an outside air temperature. The control device correctsthe target evaporation temperature to be high when the outside airtemperature detected by the outside air temperature sensor is high, andcorrects the target evaporation temperature in the region of the hightemperature of the cooled space detected by the cooled state sensorbased on the outside air temperature. Thus, it is possible to achievemore accurate rotational speed control.

1. A cooling apparatus comprising: a refrigerant circuit which includesa compressor capable of controlling a speed of rotation, and uses acarbon dioxide refrigerant; a control device which controls a speed ofrotation of the compressor; and a cooled state sensor capable ofdetecting a cooled state of a space to be cooled by an evaporatorincluded in the refrigerant circuit, wherein the control device sets atarget evaporation temperature of the refrigerant at the evaporatorbased on a temperature of the cooled space detected by the cooled statesensor, and controls the speed of rotation of the compressor so as toset an evaporation temperature of the refrigerant equal to the targetevaporation temperature at the evaporator, wherein the control devicesets the target evaporation temperature of the refrigerant at theevaporator in a relation of being higher as the temperature of thecooled space is higher based on the temperature of the cooled spacedetected by the cooled state sensor; wherein the control device sets thetarget evaporation temperature in a relation of being small in changethereof which accompanies a change in the temperature of the cooledspace in a region of a high temperature of the cooled space detected bythe cooled state sensor, and large in change thereof which accompanies achange in the temperature of the cooled space in a region of a lowtemperature of the cooled space.